Hydraulic system for coordinated operation of multiple work devices in track engineering vehicle

Abstract

Provided is a hydraulic system for coordinated operation of multiple work devices in a track engineering vehicle, comprising a hydraulic power pump set, a load-sensitive hydraulic variable circuit and a hydraulic constant-flow circuit installed on a vehicle frame; an oil outlet pipe P0 in the hydraulic power pump set is in communication with an oil inlet in the load-sensitive hydraulic variable circuit, and an oil outlet in the load-sensitive hydraulic variable circuit is in communication with an oil return pipe R0 of the hydraulic power pump set; two parallel oil outlet pipes P1 and P2 in the hydraulic power pump set are in communication with corresponding oil inlets in the hydraulic constant-flow circuit, and an oil return pipe R1 and an oil return pipe R2 in the hydraulic power pump set are in communication with corresponding oil return ports in the hydraulic constant-flow circuit. The present application realizes the cooperation and composite linkage of the operation of a scissor lifting platform work device, a rotary lifting telescopic platform work device and a vehicle locking device, improves the stability of operation and the comfort of the operator, realizes the hydraulic emergency reset measure in the case of hydraulic power or electrical failure, and improves the safety of vehicle operation.

Description

Technical Field

[0001] This invention belongs to the field of railway engineering machinery technology, specifically relating to a hydraulic system for the coordinated operation of multiple working devices in a track engineering vehicle. Background Technology

[0002] With the continuous improvement of the scale, operating speed, operating mileage, and operating frequency of urban rail transit in my country, the workload of line maintenance and repair has increased accordingly, leading to a growing demand for vehicles capable of meeting the needs of urban rail line maintenance. Faced with the complex maintenance conditions of railway overhead contact lines, the single working devices and hydraulic systems of existing track engineering vehicles are no longer sufficient to meet the needs of comprehensive, multi-area maintenance. Existing track engineering vehicles are often equipped with multiple working devices for multi-point, multi-faceted collaborative maintenance operations, such as... Figure 1 As shown, the operating device includes a scissor lift platform operating device, a rotary telescopic platform operating device, and a vehicle locking device. The scissor lift platform operating device includes a scissor platform lifting mechanism 1, a scissor guardrail lifting mechanism 2, a scissor platform guardrail locking mechanism 3, a scissor platform locking mechanism 4, and a scissor platform ramp retraction mechanism 5. The rotary telescopic platform operating device includes a rotary platform ramp retraction mechanism 6, a rotary platform guardrail lifting mechanism 7, a rotary platform guardrail locking mechanism 8, a rotary telescopic platform locking mechanism 9, a telescopic platform guardrail locking mechanism 10, a telescopic platform guardrail lifting mechanism 11, a rotary platform telescopic mechanism 12, an auxiliary platform guardrail lifting mechanism 13, and an auxiliary platform guardrail lock. The system includes a fixed mechanism 14, an auxiliary platform lifting mechanism 15, an auxiliary platform locking mechanism 16, a rotating platform slewing mechanism 17, a rotating platform leveling mechanism 18, a rotating platform leveling and locking mechanism 19, and a rotating platform lifting mechanism 20; the vehicle locking device includes a vehicle secondary system lock 21 and a vehicle primary system lock 22; the actuators in the above-mentioned working device are driven by a hydraulic quantitative system. When the operator stands on the working platform, the hydraulic valve controlled by the switch quantity opens or closes instantaneously, resulting in large impacts, poor stability, and unadjustable operating speed when the mechanism starts and stops, which seriously affects the stability of the actuator and the comfort of the operator. Therefore, it is necessary to improve the above-mentioned problems. Summary of the Invention

[0003] The technical problem solved by this invention is to provide a hydraulic system for the coordinated operation of multiple working devices in a rail engineering vehicle. This system employs a combination of load-sensitive variable hydraulic circuits and fixed hydraulic circuits. The load-sensitive variable hydraulic circuit controls lifting, rotating, extending, and leveling actions that affect operator comfort, offering advantages such as controllable speed, precise control, and smooth, shock-free operation. It also enables high-precision synchronous lifting actions of multiple working devices with different structural forms, improving system performance and operator comfort. Meanwhile, the fixed hydraulic circuits, which do not affect operator comfort, utilize on / off control for actuators such as railings, ramps, and locks. Individual actuators can operate, or corresponding solenoid valves can be energized simultaneously to achieve simultaneous lifting and lowering of railings, locking and unlocking, and simultaneous extension and retraction of ramps. The impact of these actions does not affect operator comfort, while simultaneously improving work efficiency and the cost-effectiveness of the hydraulic system.

[0004] The technical solution adopted in this invention is a hydraulic system for the coordinated operation of multiple working devices in a rail engineering vehicle, comprising a hydraulic power pump unit installed at the bottom of the vehicle frame, a load-sensitive hydraulic variable circuit and a hydraulic quantitative circuit installed on the frame; the oil outlet pipe P0 of the hydraulic power pump unit is connected to the oil inlet of the load-sensitive hydraulic variable circuit, and the oil outlet of the load-sensitive hydraulic variable circuit is connected to the oil return pipe R0 of the hydraulic power pump unit; the two parallel oil outlet pipes P1 and P2 of the hydraulic power pump unit are connected to the corresponding oil inlets of the hydraulic quantitative circuit; and the oil return pipes R1 and R2 of the hydraulic power pump unit are connected to the corresponding oil return ports of the hydraulic quantitative circuit.

[0005] The hydraulic actuators in the multi-operation device on the vehicle are divided into a first hydraulic actuator section that affects the comfort of the operator and a second hydraulic actuator section that does not affect the comfort of the operator. The hydraulic actuators in the first hydraulic actuator section are connected in parallel to the load-sensitive hydraulic variable circuit, and the actuators in the second hydraulic actuator section are connected in parallel to the hydraulic quantitative circuit. Under the control of the load-sensitive hydraulic variable circuit and the hydraulic quantitative circuit, the coordinated action of the hydraulic actuators in the multi-operation device is realized.

[0006] The hydraulic power pump unit includes hydraulic pump one and hydraulic pump two. The suction ports of hydraulic pump one and hydraulic pump two are connected to the hydraulic oil tank via suction filters. The outlet port of hydraulic pump one is connected to outlet pipe P0 via an oil pipe equipped with a check valve and a high-pressure pipeline filter. An unloading pipe one connected to outlet pipe P0 is also connected to a hydraulic return oil integrated block. The hydraulic return oil integrated block is connected to the hydraulic oil tank via an oil pipe equipped with a return oil filter. The outlet port of hydraulic pump two is connected to a hydraulic return oil integrated block via an oil pipe equipped with a check valve and a high-pressure pipeline filter. The oil pipe of the pipeline filter is connected to the parallel oil outlet pipes P1 and P2. The unloading pipe two, which is connected to the oil outlet pipes P1 and P2, is connected to the hydraulic oil tank. Both the unloading pipe one and the unloading pipe two are equipped with shut-off valves and unloading valves. The unloading pipe two is equipped with a return oil filter. The hydraulic return oil integrated block is connected to the return oil pipes T1, R0 and R2. The return oil pipe R1 is connected to the hydraulic oil tank, and the drain pipes Y and L are connected to the hydraulic oil tank through the integrated oil circuit block.

[0007] Furthermore, the hydraulic power pump set also includes an electric emergency pump and a hand-cranked manual pump. The oil suction ports of the electric emergency pump and the hand-cranked manual pump are connected to the hydraulic oil tank through an oil suction filter. The oil outlet of the electric emergency pump is connected to the oil inlet of a Y-shaped oil pipe equipped with a one-way valve. One oil outlet port of the Y-shaped oil pipe is unidirectionally connected to the oil outlet pipe P0. The other oil outlet of the U-shaped oil pipe is connected to the oil outlet pipe P2 and the unloading pipe two. An overflow valve one is installed on the other oil outlet of the Y-shaped oil pipe.

[0008] Furthermore, the load-sensitive hydraulic variable circuit adopts an open-type load-sensitive hydraulic variable circuit. The open-type load-sensitive hydraulic variable circuit includes multiple load-sensitive reversing lines and a follow-up pressure control module for controlling the oil pressure of the multiple load-sensitive reversing lines according to the load. The multiple load-sensitive reversing lines are connected in parallel to the high-pressure line of the follow-up pressure control module, and the multiple load-sensitive reversing lines are respectively connected to each hydraulic actuator in the first hydraulic actuation part. The oil inlet of the follow-up pressure control module is connected to the oil outlet pipe P0 in the hydraulic power pump group, and the control oil required in the multiple load-sensitive reversing lines is taken from the oil outlet pipe P0.

[0009] Furthermore, the follow-up pressure control module includes a pressure compensation valve one, a pilot control valve, and a relief valve two. The two ends of the oil pipe with the relief valve two are connected to the upstream oil outlet pipe P0 and the return oil pipe R0, respectively. The two ends of the oil pipe located downstream of the relief valve two and equipped with the pressure compensation valve one are connected to the oil outlet pipe P0 and the return oil pipe R0, respectively. The pressure compensation valve one is connected to the load pressure pipe LS, and the working pressure in the oil outlet pipe P0 is automatically compensated by the pressure compensation valve one according to the load feedback on the load pressure pipe LS. The sensitive hydraulic oil pipe located downstream of the pressure compensation valve one and equipped with the pilot control valve is connected to the oil outlet pipe P0, and the pressure relief line of the pilot control valve is connected to the drain pipe Y. Multiple load-sensitive reversing lines are connected in parallel on the sensitive hydraulic oil pipe downstream of the pilot control valve.

[0010] Furthermore, the load-sensitive reversing pipeline includes an electro-proportional pressure reducing valve one, an electro-proportional pressure reducing valve two, a pressure compensation valve two, and a reversing valve one. The oil pipe with the electro-proportional pressure reducing valve one installed and the oil pipe with the electro-proportional pressure reducing valve two installed are connected in parallel at one end to the sensitive hydraulic oil pipe, while the other end is connected to the corresponding interface of the reversing valve one. The upstream end of the oil pipe with the pressure compensation valve two installed is connected to the load pressure pipe LS through a shuttle valve. The control oil of the pressure compensation valve two is taken from the outlet oil pipe P0, and the downstream end of the pressure compensation valve two is connected to the reversing valve one. The two interfaces of the reversing valve one are connected to the rodless chamber and the rod chamber of the corresponding hydraulic actuator in the first hydraulic actuation part through oil pipes, respectively, and the oil direction of the two interfaces of the reversing valve one is switched according to the electrical signals of the electro-proportional pressure reducing valve one and the electro-proportional pressure reducing valve two.

[0011] The oil pipes connected to the two ports of the first directional valve and the control oil in the first directional valve are respectively connected to the return oil pipe R0 through the relief valve third; the first directional valve is a three-position seven-way directional valve.

[0012] Furthermore, the first hydraulic actuator includes multiple hydraulic cylinders in the scissor lift mechanism, multiple hydraulic cylinders in the rotary platform lift mechanism, multiple hydraulic cylinders in the rotary platform leveling mechanism, a hydraulic motor in the rotary platform slewing mechanism, multiple hydraulic cylinders in the rotary platform telescopic mechanism, and a hydraulic cylinder in the auxiliary platform lift mechanism. The rodless chamber and rod chamber of the multiple hydraulic cylinders in the scissor lift mechanism, rotary platform lift mechanism, rotary platform leveling mechanism, rotary platform telescopic mechanism, and auxiliary platform lift mechanism are respectively connected to the oil supply pipe in the corresponding load-sensitive reversing pipeline. The two oil ports of the hydraulic motor in the rotary platform slewing mechanism are respectively connected to the two oil pipes in the corresponding load-sensitive reversing pipeline. The multiple hydraulic cylinders in the scissor lift mechanism, rotary platform lift mechanism, and auxiliary platform lift mechanism are all connected to the return oil pipe T1 through an oil pipe equipped with an emergency drain valve. The hydraulic motor in the rotary platform slewing mechanism is connected to the drain pipe L through an oil pipe.

[0013] Furthermore, the hydraulic metering circuit includes a hydraulic metering circuit one and a hydraulic metering circuit two. The high-pressure oil port of the hydraulic metering circuit one is connected to the oil outlet pipe P1, and the oil return port of the hydraulic metering circuit one is connected to the oil return pipe R1. The high-pressure oil port of the hydraulic metering circuit two is connected to the oil outlet pipe P2, and the oil return port of the hydraulic metering circuit two is connected to the oil return pipe R2.

[0014] Furthermore, the hydraulic quantitative circuit one includes a reversing valve two, a main relief valve, a multi-way reversing oil inlet connection one, and a multi-way reversing oil inlet connection two. The reversing valve two, which is in a closed state when de-energized, is installed on the upstream section of the working oil pipe, and the upstream end of the working oil pipe is connected to the outlet oil pipe P1. The oil inlets of the multi-way reversing oil inlet connection one and the multi-way reversing oil inlet connection two are connected in parallel to the working oil pipe. The main relief valve, which is used to limit the maximum working pressure on the control circuit of the hydraulic quantitative circuit one, is connected to the outlet oil pipe P1 and the return oil pipe R1, and the return oil ports of the multi-way reversing oil inlet connection one and the multi-way reversing oil inlet connection two are connected to the return oil pipe R1.

[0015] The reversing oil inlet valve 1 includes a three-position four-way solenoid reversing valve 1. The oil inlet and return port of the three-position four-way solenoid reversing valve 1 are connected to the oil outlet pipe P1 and the oil return pipe R1, respectively. The two working oil ports of the three-position four-way solenoid reversing valve 1 are connected to the rodless chamber and rod chamber of the corresponding hydraulic actuator in the second hydraulic actuator part through the oil supply pipes of two parallel overflow valves 4 with opposite flow directions.

[0016] The second reversing oil inlet includes a three-position four-way solenoid reversing valve and a one-way throttle valve. The oil inlet and return port of the two-position four-way solenoid reversing valve are connected to the oil outlet pipe P1 and the oil return pipe R1, respectively. The two working oil ports of the two-position four-way solenoid reversing valve are connected to the rodless chamber and rod chamber of the corresponding hydraulic actuator in the second hydraulic actuation part through two oil supply pipes with one-way throttle valves installed.

[0017] The hydraulic quantitative circuit two includes a multi-way reversing oil inlet link three, with the inlets of the multiple reversing oil inlet links three connected in parallel to the outlet pipe P2, and the return ports of the multiple reversing oil inlet links three connected in parallel to the return pipe R2; the working pressure switching valve group includes a solenoid reversing valve and two relief valves five connected in parallel to the two working oil port pipes of the solenoid reversing valve, with the inlet of the solenoid reversing valve connected to the upstream section of the outlet pipe P2, and the return port of the solenoid reversing valve connected to the downstream section of the return pipe R2.

[0018] The reversing oil inlet link three and the multi-way reversing oil inlet link two have the same structure.

[0019] Furthermore, the second hydraulic actuation unit includes multiple hydraulic cylinders in the vehicle primary locking system, multiple hydraulic cylinders in the vehicle secondary locking system, multiple hydraulic cylinders in the auxiliary platform guardrail lifting mechanism, multiple hydraulic cylinders in the telescopic platform guardrail lifting mechanism, multiple hydraulic cylinders in the rotating platform guardrail lifting mechanism, multiple hydraulic cylinders in the scissor lift guardrail lifting mechanism, multiple hydraulic cylinders in the scissor lift platform guardrail locking mechanism, multiple hydraulic cylinders in the scissor lift platform locking mechanism, multiple hydraulic cylinders in the scissor lift platform ramp retraction mechanism, and multiple hydraulic cylinders in the rotating platform ramp retraction mechanism, multiple hydraulic cylinders in the rotating platform guardrail locking mechanism, multiple hydraulic cylinders in the telescopic platform guardrail locking mechanism, multiple hydraulic cylinders in the auxiliary platform guardrail locking mechanism, multiple hydraulic cylinders in the rotating telescopic platform locking mechanism, multiple hydraulic cylinders in the rotating platform leveling locking mechanism, and multiple hydraulic cylinders in the auxiliary platform locking mechanism; wherein, Multiple hydraulic cylinders in the vehicle's primary locking system are connected in parallel to one of the oil supply pipes of the reversing oil inlet connector 1. Multiple hydraulic cylinders in the vehicle's secondary locking system are connected in parallel to another oil supply pipe of the reversing oil inlet connector 1. Multiple hydraulic cylinders in the auxiliary platform guardrail lifting mechanism, telescopic platform guardrail lifting mechanism, rotating platform guardrail lifting mechanism, scissor lift guardrail lifting mechanism, scissor platform guardrail locking mechanism, scissor platform locking mechanism, and scissor platform ramp retraction mechanism are connected in parallel to the corresponding reversing oil inlet connector 2 oil supply pipes. The two oil supply pipes of the multiple reversing oil inlet connector 2, which are connected in parallel to multiple hydraulic cylinders in the auxiliary platform guardrail lifting mechanism, telescopic platform guardrail lifting mechanism, rotating platform lifting mechanism, and scissor lift mechanism, are connected through an oil pipe equipped with a one-way balance valve to limit the descent speed of the cylinders. One of the oil supply pipes is connected to the return oil pipe T1 through an emergency oil pipe equipped with an emergency drain valve 1.

[0020] The oil supply pipes of the multi-way reversing oil inlet joint are respectively connected to the hydraulic cylinders in the rotating platform plate retraction mechanism, rotating platform guardrail locking mechanism, telescopic platform guardrail locking mechanism, auxiliary platform guardrail locking mechanism, rotating telescopic platform locking mechanism, rotating platform leveling locking mechanism, and auxiliary platform locking mechanism.

[0021] Advantages of this invention compared to existing technologies:

[0022] 1. This technical solution provides hydraulic power through hydraulic power pump group A, and adopts a combination of load-sensitive hydraulic variable circuit and hydraulic quantitative circuit to realize the coordinated and compound linkage of the scissor lift platform working device, the rotary lifting telescopic platform working device and the vehicle locking device, thereby improving the stability of the operation and the comfort of the operators.

[0023] 2. This technical solution categorizes the working devices according to whether they affect the comfort of the workers. Actions affecting worker comfort, such as lifting, rotating, extending, and leveling, are controlled using load-sensitive hydraulic variable circuits. This offers advantages such as controllable speed, precise control, and smooth, shock-free operation. It also enables high-precision synchronous lifting actions of multiple working devices with different structural forms, improving system performance and worker comfort. Meanwhile, actuators that do not affect worker comfort, such as railings, ramps, and locks, utilize on / off controlled hydraulic quantitative circuits. These can operate individually or simultaneously by energizing corresponding solenoid valves, achieving simultaneous lifting and lowering of railings, locking and unlocking, and simultaneous extension and retraction of ramps. The impact of these actions will not affect worker comfort, while simultaneously improving work efficiency and the cost-effectiveness of the hydraulic system.

[0024] 3. The design of the emergency drain valve in this technical solution allows the valve core to be activated by pushing the button or mechanical handle on the emergency drain valve, thereby achieving emergency reset of the corresponding action. The lowering of the barrier can be achieved by opening the emergency drain valve, realizing hydraulic emergency reset measures in the event of hydraulic power or electrical failure, so as to improve the safety of vehicle operation. Attached Figure Description

[0025] Figure 1 A schematic diagram showing the location and structure of the working devices on a rail engineering vehicle;

[0026] Figure 2 This is a control principle diagram of the hydraulic power pump unit of the present invention;

[0027] Figure 3 This is a schematic diagram of the load-sensitive hydraulic variable loop control principle of the present invention;

[0028] Figure 4 This is a schematic diagram of the hydraulic quantitative circuit control principle of the present invention;

[0029] Figure 5 This is a control principle diagram of the hydraulic quantitative circuit two of the present invention. Detailed Implementation

[0030] The following will be based on embodiments of the present invention. Figures 2-5 The technical solutions in the embodiments of the present invention are clearly and completely described herein. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0031] It should be noted that, in this document, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0032] The hydraulic system for the coordinated operation of multiple working devices in a rail engineering vehicle includes a hydraulic power pump group A installed at the bottom of the vehicle frame and powered by the engine through a transfer case, a load-sensitive hydraulic variable circuit B and a hydraulic metering circuit installed on the frame; the oil outlet pipe P0 of the hydraulic power pump group A is connected to the oil inlet of the load-sensitive hydraulic variable circuit B, and the oil outlet of the load-sensitive hydraulic variable circuit B is connected to the oil return pipe R0 of the hydraulic power pump group A; the two parallel oil outlet pipes P1 and P2 of the hydraulic power pump group A are connected to the corresponding oil inlets of the hydraulic metering circuit; and the oil return pipes R1 and R2 of the hydraulic power pump group A are connected to the corresponding oil return ports of the hydraulic metering circuit.

[0033] The hydraulic actuators in the multi-operation device on the vehicle are divided into a first hydraulic actuator section that affects the comfort of the operator and a second hydraulic actuator section that does not affect the comfort of the operator. The hydraulic actuators in the first hydraulic actuator section are connected in parallel to the load-sensitive hydraulic variable circuit B, and the actuators in the second hydraulic actuator section are connected in parallel to the hydraulic metering circuit. Under the control of the load-sensitive hydraulic variable circuit B and the hydraulic metering circuit, the coordinated action of the hydraulic actuators in the multi-operation device is realized.

[0034] like Figure 2As shown, the specific structure of the hydraulic power pump group A is as follows: The hydraulic power pump group A includes hydraulic pump A1 and hydraulic pump A2. The oil suction ports of hydraulic pump A1 and hydraulic pump A2 are connected to the hydraulic oil tank A4 through the oil suction filter A3. The oil outlet of hydraulic pump A1 is connected to the oil outlet pipe P0 through an oil pipe equipped with a check valve A17 and a high-pressure pipeline filter A5. The unloading pipe A6 connected to the oil outlet pipe P0 is connected to the hydraulic return oil integration block A7. The hydraulic return oil integration block A7 is connected to the hydraulic oil tank A4 through an oil pipe equipped with a return oil filter A11. The oil outlet of hydraulic pump A2 is connected to the hydraulic oil tank A4 through an oil pipe equipped with a return oil filter A11. The oil pipe equipped with a one-way valve A17 and a high-pressure pipeline filter A5 is connected to the parallel oil outlet pipes P1 and P2. The unloading pipe A8, which is connected to the oil outlet pipes P1 and P2, is connected to the hydraulic oil tank A4. The unloading pipe A6 and the unloading pipe A8 are both equipped with a shut-off valve A9 and an unloading valve A10. The unloading pipe A8 is equipped with a return oil filter A11. The hydraulic return oil integrated block A7 is connected to the return oil pipes T1, R0, and R2. The return oil pipe R1 is connected to the hydraulic oil tank A4. The drain pipes Y and L are connected to the hydraulic oil tank A4 through the integrated oil circuit block A16.

[0035] In the above structure of hydraulic power pump group A, the power is taken from the vehicle transfer case to drive hydraulic pump one A1 and hydraulic pump two A2 to rotate, and draw oil from the suction filter A3 connected to them. The oil from hydraulic pump one A1 is filtered through high pressure pipeline filter A5, and then through the shut-off valve A9 and unloading valve A10 on unloading pipe one A6 to the hydraulic return oil integration block A7 and return oil filter A11 to return to the hydraulic oil tank A4. The oil from hydraulic pump two A2 is filtered through high pressure pipeline filter A5, and then through the shut-off valve A9, unloading valve A10 and return oil filter A11 on unloading pipe two A8 to return to the hydraulic oil tank A4. Check valve A17 is used to isolate the entire power circuit. At this time, the system is in the unloaded state.

[0036] During operation, the unloading valve A10 on unloading pipe A6 is energized and closed, and the working oil is output to the load-sensitive hydraulic variable circuit B through the oil outlet pipe P0 circuit. The unloading valve A10 on unloading pipe A8 is energized and closed, and the working oil is output to the hydraulic quantitative circuit C1 through the oil outlet pipe P1 circuit. At this time, it is in a low-pressure standby state.

[0037] To prevent the system from malfunctioning when hydraulic pumps A1 and A2 fail, the following structure is designed: The hydraulic power pump group A also includes an electric emergency pump A12 and a hand-cranked manual pump A13. The oil suction ports of the electric emergency pump A12 and the hand-cranked manual pump A13 are connected to the hydraulic oil tank A4 through the oil suction filter A3. The oil outlet of the electric emergency pump A12 is connected to the oil inlet of the Y-shaped oil pipe A14, which is equipped with a one-way valve A17. One oil outlet port of the Y-shaped oil pipe A14 is connected to the oil outlet pipe P0 in one direction. The other oil outlet of the U-shaped oil pipe A14 is connected to the oil outlet pipe P2 and the unloading pipe A8. An overflow valve A15 is installed on the other oil outlet of the Y-shaped oil pipe A14.

[0038] If hydraulic pump A1 and hydraulic pump A2 malfunction, they can be replaced by starting the electric emergency pump A12 or the hand-cranked manual pump A13. If the electrical control system malfunctions and the unloading valves A10 on unloading pipe A6 and A8 cannot be energized and closed, the shut-off valves A9 on unloading pipe A6 and A8 can be closed as an emergency replacement. The relief valve A15 acts as an emergency circuit pressure protection. When the pressure in the emergency pipeline (i.e., Y-type oil pipe A14) is too high and exceeds the rated value of the relief valve A15, the relief valve A15 connects to the downstream end of the load pipe A8, and the oil returns to the hydraulic oil tank A4. Hydraulic pumps A1 and A2 can be driven by the vehicle transfer case, or by an AC motor, diesel engine, etc.

[0039] like Figure 3 As shown, the specific structure of the load-sensitive hydraulic variable circuit B is as follows: The load-sensitive hydraulic variable circuit B adopts an open-type load-sensitive hydraulic variable circuit. The open-type load-sensitive hydraulic variable circuit includes multiple load-sensitive reversing pipelines B1 and a follow-up pressure control module B2 for controlling the oil pressure of the multiple load-sensitive reversing pipelines B1 according to the load. The multiple load-sensitive reversing pipelines B1 are connected in parallel to the high-pressure pipeline of the follow-up pressure control module B2, and the multiple load-sensitive reversing pipelines B1 are respectively connected to each hydraulic actuator in the first hydraulic actuation part. The oil inlet of the follow-up pressure control module B2 is connected to the oil outlet pipe P0 in the hydraulic power pump group A, and the control oil required in the multiple load-sensitive reversing pipelines B1 is taken from the oil outlet pipe P0.

[0040] The specific structure of the follow-up pressure control module B2 is as follows: The follow-up pressure control module B2 includes a pressure compensation valve B2-1, a pilot control valve B2-2, and a relief valve B2-3. The two ends of the oil pipe with the relief valve B2-3 installed are connected to the upstream outlet pipe P0 and the return pipe R0, respectively. The two ends of the oil pipe located downstream of the relief valve B2-3 and equipped with the pressure compensation valve B2-1 are connected to the outlet pipe P0 and the return pipe R0, respectively. The pressure compensation valve B2-1 is connected to the load pressure pipe... LS is connected, and the working pressure in the outlet pipe P0 is automatically compensated by the pressure compensation valve B2-1 according to the load feedback on the load pressure pipe LS; the sensitive hydraulic oil pipe B2-4, located downstream of the pressure compensation valve B2-1 and equipped with the pilot control valve B2-2, is connected to the outlet pipe P0, and the pressure relief line of the pilot control valve B2-2 is connected to the drain pipe Y. Multiple load-sensitive reversing lines B1 are connected in parallel on the sensitive hydraulic oil pipe B2-4 downstream of the pilot control valve B2-2.

[0041] The specific structure of the load-sensitive directional control line B1 is as follows: The load-sensitive directional control line B1 includes an electro-proportional pressure reducing valve B1-1, an electro-proportional pressure reducing valve B1-2, a pressure compensation valve B1-3, and a directional control valve B1-4. One end of the oil pipe with the electro-proportional pressure reducing valve B1-1 and the oil pipe with the electro-proportional pressure reducing valve B1-2 are connected in parallel to the sensitive hydraulic oil pipe B2-4, while the other end is connected to the corresponding interface of the directional control valve B1-4. The upstream end of the oil pipe with the pressure compensation valve B1-3 is connected to the load pressure pipe LS through a shuttle valve B1-5. The control oil of the pressure compensation valve B1-3 is taken from the outlet oil pipe P0. Furthermore, the downstream end of pressure compensation valve B1-3 is connected to directional valve B1-4. The two ports of directional valve B1-4 are connected to the rodless chamber and rod chamber of the corresponding hydraulic actuator in the first hydraulic actuation part through oil pipes, respectively. The oil direction of the two ports of directional valve B1-4 is switched according to the electrical signals of electro-proportional pressure reducing valve B1-1 and electro-proportional pressure reducing valve B1-2. The oil pipes connected to the two ports of directional valve B1-4 and the control oil in directional valve B1-4 are connected to the return oil pipe R0 through the overflow valve B1-6. directional valve B1-4 is a three-position seven-way directional valve.

[0042] The specific connection structure between the first hydraulic actuator and the load-sensitive hydraulic variable circuit B is as follows: The first hydraulic actuator includes multiple hydraulic cylinders in the scissor lift mechanism 1, multiple hydraulic cylinders in the rotary platform lift mechanism 20, multiple hydraulic cylinders in the rotary platform leveling mechanism 18, a hydraulic motor in the rotary platform slewing mechanism 17, multiple hydraulic cylinders in the rotary platform telescopic mechanism 12, and hydraulic cylinders in the auxiliary platform lift mechanism 15. The multiple hydraulic cylinders in the scissor lift mechanism 1, the rotary platform lift mechanism 20, the rotary platform leveling mechanism 18, the rotary platform telescopic mechanism 12, and the auxiliary platform... The rodless chamber and rod chamber of the hydraulic cylinder in the lifting mechanism 15 are respectively connected to the oil supply pipe in the corresponding load-sensitive reversing pipeline B1. The two oil ports of the hydraulic motor in the rotating platform slewing mechanism 17 are respectively connected to the two oil pipes in the corresponding load-sensitive reversing pipeline B1. Among them, the multiple hydraulic cylinders in the scissor platform lifting mechanism 1, the multiple hydraulic cylinders in the rotating platform lifting mechanism 20, and the hydraulic cylinders in the auxiliary platform lifting mechanism 15 are all connected to the return oil pipe T1 through the oil pipe equipped with the emergency drain valve B3. The hydraulic motor in the rotating platform slewing mechanism 17 is connected to the drain pipe L through the oil pipe. The emergency drain valve B3 can also be replaced by a ball valve.

[0043] The first hydraulic actuator is equipped with a height measuring sensor for measuring the extension and retraction of each hydraulic cylinder. Based on the height difference detected by each height measuring sensor, the electrical signal magnitudes of the electro-proportional pressure reducing valve B1-1 and electro-proportional pressure reducing valve B1-2 are adjusted to achieve precise adjustment of the height of the corresponding actuator, thereby achieving precise synchronization of each actuator.

[0044] The mechanism affecting the comfort of the staff is controlled by the load-sensitive hydraulic variable circuit B mentioned above, so that its action speed is controllable, the control is precise, and the action is smooth. The oil output from the oil outlet pipe P0 in the hydraulic power pump group A enters the load-sensitive hydraulic variable circuit B. When the mechanism is not in motion, there is no feedback from the load pressure pipe LS. The oil pressure switches the pressure compensation valve B2-1 to the left position, only overcoming its spring setting force, and returns to the hydraulic oil tank A4 through the return oil pipe R0. The relief valve B2-3 can ensure that the maximum working pressure of the system does not exceed the pressure protection limit, thereby playing a role in pressure relief protection for the pipeline when there is an impact during the start-up and stop of the mechanism, improving the comfort of the operators. At this time, the system is in a low-pressure standby state.

[0045] When the actuator in any one or more mechanisms has load feedback, the load pressure between the actuator actions selects the maximum working load pressure through shuttle valve B1-5, which pushes pressure compensation valve B2-1 to tend to close, in order to compensate for the combined force of the maximum working load pressure and the spring set pressure. The oil circuit output from the return oil pipe R0 establishes pressure, which controls the directional valve B1-4 through the pilot control valve B2-2 and the electro-proportional pressure reducing valve B1-1 and electro-proportional pressure reducing valve B1-2 circuit, thereby controlling the action of its corresponding actuator (the extension and retraction of the hydraulic cylinder or the rotation of the motor).

[0046] like Figure 3 As shown, the following example illustrates the composite synchronous lifting action (to achieve synchronous lifting and coordinated operation of the two platforms) using two different structural forms: the scissor lift mechanism 1 and the rotary lift mechanism 20 in the two working devices:

[0047] If the electro-proportional pressure reducing valves B1-1 (i.e., D101d and D102d) in the first two load-sensitive directional control lines B1 simultaneously control the directional control valve B1-4 to receive an electro-proportional signal, the oil will act on the two main valves of the directional control valve B1-4 via the control oil circuit. At this time, PA and TB in the directional control valve B1-4 will be open, and the oil will enter D1 and D2 through PA and TB of the directional control valve B1-4 via the pressure compensation valve B1-3. The oil in D1 will then flow through the diverter valve 23 (which can be replaced by a hydraulic synchronous motor). The flow is divided equally by the flow valve 23, and then enters the rodless chamber of the scissor lifting hydraulic cylinder in the scissor platform lifting mechanism 1 through the balance valve 24. The D2 oil enters the rodless chamber of the rotary platform lifting cylinder in the rotary platform lifting mechanism 20 through the balance valve 24, driving the cylinders in both mechanisms to rise. If the electro-proportional pressure reducing valve B1-2 (i.e., D101e and D102e) circuit simultaneously controls the directional valve B1-4 to give an electro-proportional signal, the oil acts on the two main valves of the directional valve B1-4 through the control oil circuit. At this time, the directional valve... When valve PB and TA of valve B1-4 are open, the hydraulic fluid passes through pressure compensation valve B1-3 to directional valve B1-4, entering E1 and E2. The hydraulic fluid in E1 enters the rod chamber of the scissor lifting hydraulic cylinder in scissor platform lifting mechanism 1 via balance valve 24, and the hydraulic fluid in E2 enters the rod chamber of the rotary platform lifting cylinder in rotary platform lifting mechanism 20 via balance valve 24, driving the hydraulic cylinders in both mechanisms to descend. Due to the different structural forms and forces, the speed before and after the lifting or lowering action will be inconsistent. Through automatic closed-loop control, the lifting height of the scissor platform and rotary platform is detected in real time using a height measurement sensor. The lifting height of the scissor platform is used as the reference height. When the lifting height of the rotary platform deviates from the reference height by ΔH, the electrical signal of D102d is adjusted in real time through automatic closed-loop control to control the opening size of the main valve core of the corresponding directional valve B1-4, adaptively increasing or decreasing the flow rate to effectively compensate for the lifting height.

[0048] The control principles of the hydraulic cylinders in the remaining rotating platform leveling mechanism 18, the hydraulic motors in the rotating platform slewing mechanism 17, the hydraulic cylinders in the rotating platform telescopic mechanism 12, and the hydraulic cylinders in the auxiliary platform lifting mechanism 15 are basically the same as the control principles of the single or combined actions of the hydraulic cylinders in the scissor lift mechanism 1 and the rotating platform lifting mechanism 20.

[0049] like Figures 4-5As shown, the specific structure of the hydraulic metering circuit is as follows: The hydraulic metering circuit includes hydraulic metering circuit one C1 and hydraulic metering circuit two C2. The high-pressure oil interface of hydraulic metering circuit one C1 is connected to the oil outlet pipe P1, and the oil return port of hydraulic metering circuit one C1 is connected to the oil return pipe R1; the high-pressure oil interface of hydraulic metering circuit two C2 is connected to the oil outlet pipe P2, and the oil return port of hydraulic metering circuit two C2 is connected to the oil return pipe R2.

[0050] Specifically, such as Figure 4 As shown, the hydraulic quantitative control circuit C1 includes a directional valve C1-1, a main relief valve C1-2, a multi-way directional inlet valve C1-3, and a multi-way directional inlet valve C1-4. The directional valve C1-1, which is closed when de-energized, is installed on the upstream section of the working oil pipe C1-5, and the upstream end of the working oil pipe C1-5 is connected to the outlet pipe P1. The inlets of the multi-way directional inlet valves C1-3 and C1-4 are connected in parallel to the working oil pipe C1-5. The main relief valve C1-2, used to limit the maximum working pressure on the hydraulic quantitative control circuit C1, is connected to the outlet pipe P1 and the return pipe R1. The return ports of the multi-way directional inlet valves C1-3 and C1-4 are connected to the return pipe R1. The directional inlet valve C1-3 includes a three-position four-way solenoid directional valve C1-31. The inlet and outlet of the three-position four-way solenoid directional valve C1-31 are connected to the outlet pipe P1 and the return pipe R1, respectively. The two working ports of the three-position four-way solenoid directional valve C1-31 are connected to the rodless and rod-side chambers of the corresponding hydraulic actuators in the second hydraulic actuation section via two parallel overflow valves C1-32 with opposite flow directions. The reversing inlet connector C1-4 includes a three-position four-way solenoid directional valve C1-41 and a one-way throttle valve C1-42. The inlet and outlet of the three-position four-way solenoid directional valve C1-41 are connected to the outlet pipe P1 and the return pipe R1, respectively. The two working ports of the three-position four-way solenoid directional valve C1-41 are connected to the rodless and rod-side chambers of the corresponding hydraulic actuators in the second hydraulic actuation section via two supply pipes housing the one-way throttle valves C1-42. Figure 5 As shown, the hydraulic quantitative circuit C2 includes a multi-way reversing oil inlet link C2-1, with the inlets of the multiple reversing oil inlet links C2-1 connected in parallel to the outlet pipe P2, and the return ports of the multiple reversing oil inlet links C2-1 connected in parallel to the return pipe R2; the working pressure switching valve group C2-2 includes a solenoid reversing valve C2-21 and two overflow valves C2-22 connected in parallel to the two working oil port pipes of the solenoid reversing valve C2-21. The inlet of the solenoid reversing valve C2-21 is connected to the upstream section of the outlet pipe P2, and the return port of the solenoid reversing valve C2-21 is connected to the downstream section of the return pipe R2; the reversing oil inlet link C2-1 and the multi-way reversing oil inlet link C1-4 have the same structure.

[0051] The specific connection between the second hydraulic actuator and the hydraulic metering circuit is as follows: The second hydraulic actuator includes multiple hydraulic cylinders in the vehicle primary locking 22, multiple hydraulic cylinders in the vehicle secondary locking 21, multiple hydraulic cylinders in the auxiliary platform guardrail lifting mechanism 13, multiple hydraulic cylinders in the telescopic platform guardrail lifting mechanism 11, multiple hydraulic cylinders in the rotating platform guardrail lifting mechanism 7, multiple hydraulic cylinders in the scissor lift guardrail lifting mechanism 2, multiple hydraulic cylinders in the scissor platform guardrail locking mechanism 3, multiple hydraulic cylinders in the scissor platform locking mechanism 4, multiple hydraulic cylinders in the scissor platform ramp retraction mechanism 5, multiple hydraulic cylinders in the rotating platform ramp retraction mechanism 6, multiple hydraulic cylinders in the rotating platform guardrail locking mechanism 8, multiple hydraulic cylinders in the telescopic platform guardrail locking mechanism 10, multiple hydraulic cylinders in the auxiliary platform guardrail locking mechanism 14, multiple hydraulic cylinders in the rotating telescopic platform locking mechanism 9, hydraulic cylinders in the rotating platform leveling locking mechanism 19, and hydraulic cylinders in the auxiliary platform locking mechanism 16; wherein, the... Multiple hydraulic cylinders in the vehicle primary locking system 22 are connected in parallel to the oil supply pipe of one of the reversing oil inlet lines C1-3. Multiple hydraulic cylinders in the vehicle secondary locking system 21 are connected in parallel to the oil supply pipe of another reversing oil inlet line C1-3. Multiple hydraulic cylinders in the auxiliary platform guardrail lifting mechanism 13, telescopic platform guardrail lifting mechanism 11, rotating platform guardrail lifting mechanism 7, scissor lift guardrail lifting mechanism 2, scissor platform guardrail locking mechanism 3, scissor platform locking mechanism 4, and scissor platform ramp retraction mechanism 5 are also connected in parallel to the oil supply pipe of the other reversing oil inlet line C1-3. Connected to the corresponding reversing oil inlet connector C1-4 oil supply pipe; the multi-way reversing oil inlet connector C1-4 is connected to two oil supply pipes that are connected in parallel to multiple hydraulic cylinders in the auxiliary platform guardrail lifting mechanism 13, telescopic platform guardrail lifting mechanism 11, rotating platform guardrail lifting mechanism 7 and scissor guardrail lifting mechanism 2 through an oil pipe equipped with a one-way balance valve C1-43 and used to limit the descent speed of the oil cylinder, and one of the oil supply pipes is connected to the return oil pipe T1 through an emergency oil pipe equipped with an emergency oil drain shut-off valve C1-44;

[0052] The oil supply pipes of the multi-way reversing oil inlet joint C2-1 are respectively connected to the hydraulic cylinders in the rotating platform plate retraction mechanism 6, rotating platform guardrail locking mechanism 8, telescopic platform guardrail locking mechanism 10, auxiliary platform guardrail locking mechanism 14, rotating telescopic platform locking mechanism 9, rotating platform leveling locking mechanism 19, and auxiliary platform locking mechanism 16.

[0053] The working principle of the hydraulic quantitative circuit is as follows: The parallel oil outlet pipes P1 and P2 output from the hydraulic power pump group A enter the hydraulic quantitative circuit one C1 and the hydraulic quantitative circuit two C2 respectively; the oil entering the hydraulic quantitative circuit two C2 passes through the M-function three-position four-way solenoid directional valve two C1-41 in the multi-way reversing oil inlet link three C2-1 and returns to the hydraulic oil tank A4 via the return oil pipe R2. At this time, the system is in a low-pressure standby state; when the system is working, the M-function three-position four-way solenoid directional valve C2-21 is energized in the left or right position, which can switch the required working overflow pressure of the overflow valve five C2-22. At this time, the system is in a high-pressure standby state. The overflow pressure is determined by the minimum set value of the main overflow valve C1-2 and the overflow valve five C2-22. The pressure gauge one C1-6 on the oil outlet pipe P1 and the pressure gauge two C2-3 on the oil outlet pipe P2 can measure the working pressure in the hydraulic quantitative circuit one C1 and the hydraulic quantitative circuit two C2 system respectively.

[0054] During coordinated operation, firstly, D201e and D202e of the three-position four-way solenoid directional valve C1-31 of the two-way reversing oil inlet line C1-3 are simultaneously energized. This energizes the hydraulic cylinders in the vehicle's primary locking system 22 and secondary locking system 21 via the oil supply pipes D7 and D8 of the solenoid directional valve C1-31 of the two-way reversing oil inlet line C1-3, respectively, achieving rigid vehicle locking. At this time, E7 of the solenoid directional valve C1-31 of the one-way reversing oil inlet line C1-3 and E8 of the solenoid valve C1-31 of the other-way reversing oil inlet line C1-3 both function as return oil. Then, the fifth cylinder from the left in the hydraulic metering circuit C1... The Y-function three-position four-way solenoid directional valves D207d and D208d in the six-way reversing oil inlet link C1-4 and the Y-function three-position four-way solenoid directional valves D303d, D304d, D305d, D306d, D307d, and D308d in the hydraulic quantitative circuit C2 (the 2nd to 7th reversing oil inlet links C2-1) are simultaneously electrically controlled. Oil flows through oil supply pipes E14, E15, E18, E19, E20, E21, E22, and E23 to control multiple hydraulic cylinders in the corresponding scissor lift platform guardrail locking mechanisms 3 and 4, as well as the rotating platform guardrail locking mechanism 8, the telescopic platform guardrail locking mechanism 10, the auxiliary platform guardrail locking mechanism 14, and the rotating telescopic platform. The piston rods of the hydraulic cylinders in locking mechanism 9, rotating platform leveling locking mechanism 19, and auxiliary platform locking mechanism 16 retract, unlocking all locking mechanisms. Furthermore, by simultaneously energizing D203d, D204d, D205d, and D206d of the Y-function three-position four-way solenoid directional valve C1-41 in hydraulic quantitative circuit C1 (leftmost channels 1-4), the hydraulic fluid, via E9, E10, E11, and E12, controls the extension of the hydraulic cylinder piston rods in the corresponding auxiliary platform guardrail lifting mechanism 13, telescopic platform guardrail lifting mechanism 11, rotating platform guardrail lifting mechanism 7, and scissor lift guardrail lifting mechanism 2, thus extending the left and right platform guardrails. Finally, by energizing the piston rods of the hydraulic cylinders in hydraulic quantitative circuit C1 (leftmost channel 7)... When the D209e of the Y-function three-position four-way solenoid directional valve C1-41 in the second oil inlet link C1-4 and the D302e of the Y-function three-position four-way solenoid directional valve C1-41 in the first left-hand reversing oil inlet link C2-1 in the hydraulic quantitative circuit C2 are simultaneously energized, D15 and D17 respectively control the piston rod of the scissor platform plate retraction mechanism 5 and the rotating platform plate cylinder rotating platform plate retraction mechanism 6 to extend, the plate unfolds, and the two platforms can be connected; after the synchronous hydraulic motor 25 connected to the oil supply pipe is connected to the hydraulic cylinder in the scissor guardrail lifting mechanism 2, the synchronous hydraulic motor 25 is used to synchronously operate multiple hydraulic cylinders in the scissor guardrail lifting mechanism 2, and the one-way balance valve C1-43 is used to maintain the load of each action circuit during the descent action.

[0055] If the electrical control system malfunctions, the valve core can be activated by pushing the button or mechanical handle on the emergency drain valve B3 to achieve an emergency reset of the corresponding action. The lowering of the railing can be reset by opening the emergency drain valve C1-44.

[0056] In summary, by using hydraulic power pump unit A to provide hydraulic power, and through the coordination and integration of load-sensitive variable hydraulic circuit B and hydraulic fixed-displacement circuit, the coordinated operation of all mechanisms of the scissor lift platform, the rotary lifting telescopic platform, and the vehicle locking device is achieved. Furthermore, through redundant hydraulic power design, the inclusion of mechanical handles in the control valve group, and the placement of emergency drain valves, hydraulic emergency reset measures are implemented in the event of hydraulic power or electrical failures, thereby improving vehicle operational safety. Notably, the hydraulic variable system of "fixed-displacement pump + open-type load-sensitive proportional valve" can be replaced by a hydraulic variable system of "variable pump + closed-type load-sensitive proportional valve".

[0057] This technical solution employs a combination of load-sensitive hydraulic variable circuit B and hydraulic fixed-displacement circuit. The lifting, rotating, extending, and leveling actions, which affect operator comfort, are controlled by the load-sensitive hydraulic variable circuit. This offers advantages such as controllable speed, precise control, and smooth, shock-free operation. Furthermore, it enables high-precision synchronous lifting actions of multiple operating devices with different structural forms, improving system performance and operator comfort. Meanwhile, the railings, ramps, and locking mechanisms, which do not affect operator comfort, utilize a switch-controlled hydraulic fixed-displacement circuit. Individual actuators can operate, or corresponding solenoid valves can be energized simultaneously to achieve simultaneous lifting and lowering of railings, locking and unlocking, and simultaneous extension and retraction of ramps. The impact of these actions will not affect operator comfort, while simultaneously improving work efficiency and the cost-effectiveness of the hydraulic system.

[0058] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0059] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

Claims

1. A hydraulic system for coordinated operation of multiple working devices in a rail engineering vehicle, characterized in that: The system includes a hydraulic power pump assembly (A) installed at the bottom of the vehicle frame and powered by an AC motor, diesel engine, or transfer case; a load-sensitive hydraulic variable circuit (B) and a hydraulic fixed-displacement circuit installed on the frame; the outlet pipe P0 of the hydraulic power pump assembly (A) is connected to the inlet port of the load-sensitive hydraulic variable circuit (B), and the outlet port of the load-sensitive hydraulic variable circuit (B) is connected to the return pipe R0 of the hydraulic power pump assembly (A); the two parallel outlet pipes P1 and P2 of the hydraulic power pump assembly (A) are connected to the corresponding inlet ports of the hydraulic fixed-displacement circuit; and the return pipes R1 and R2 of the hydraulic power pump assembly (A) are connected to the corresponding return ports of the hydraulic fixed-displacement circuit. Among them, the hydraulic actuators in the multi-operation device on the vehicle are divided into a first hydraulic actuator part that affects the comfort of the operator and a second hydraulic actuator part that does not affect the comfort of the operator. The hydraulic actuators in the first hydraulic actuator part are connected in parallel to the load-sensitive hydraulic variable circuit (B), and the actuators in the second hydraulic actuator part are connected in parallel to the hydraulic fixed circuit. Under the control of the load-sensitive hydraulic variable circuit (B) and the hydraulic fixed circuit, the coordinated action of the hydraulic actuators in the multi-operation device is realized. The load-sensitive hydraulic variable circuit (B) adopts an open-type load-sensitive hydraulic variable circuit, which includes multiple load-sensitive reversing lines (B1) and a follow-up pressure control module (B2) for controlling the oil pressure of multiple load-sensitive reversing lines (B1) according to the load. The follow-up pressure control module (B2) includes a pressure compensation valve (B2-1), a pilot control valve (B2-2), and a relief valve (B2-3). The pressure compensation valve (B2-1) is connected to the load pressure pipe LS, and the working pressure in the oil outlet pipe P0 is automatically compensated by the pressure compensation valve (B2-1) according to the load feedback on the load pressure pipe LS. The load-sensitive reversing pipeline (B1) includes an electro-proportional pressure reducing valve one (B1-1), an electro-proportional pressure reducing valve two (B1-2), a pressure compensation valve two (B1-3), and a reversing valve one (B1-4). The oil direction of the two ports of the reversing valve one (B1-4) is switched according to the electrical signals of the electro-proportional pressure reducing valve one (B1-1) and the electro-proportional pressure reducing valve two (B1-2). The hydraulic metering circuit includes hydraulic metering circuit one (C1) and hydraulic metering circuit two (C2); hydraulic metering circuit one (C1) includes directional valve two (C1-1), main relief valve (C1-2), multi-way directional oil inlet link one (C1-3) and multi-way directional oil inlet link two (C1-4), and directional valve two (C1-1), which is in a closed state when de-energized, is installed in the upstream section of the working oil pipe (C1-5).

2. The hydraulic system for coordinated operation of multiple working devices in a rail engineering vehicle according to claim 1, characterized in that: The hydraulic power pump assembly (A) includes hydraulic pump one (A1) and hydraulic pump two (A2). The oil inlets of hydraulic pump one (A1) and hydraulic pump two (A2) are connected to the hydraulic oil tank (A4) through an oil inlet filter (A3). The oil outlet of hydraulic pump one (A1) is connected to the oil outlet pipe P0 through an oil pipe equipped with a check valve (A17) and a high-pressure pipeline filter (A5). The unloading pipe one (A6) connected to the oil outlet pipe P0 is connected to the hydraulic return oil integrated block (A7). The hydraulic return oil integrated block (A7) is connected to the hydraulic oil tank (A4) through an oil pipe equipped with a return oil filter (A11). The oil outlet of hydraulic pump two (A2) is connected to the hydraulic oil tank (A4) through an oil pipe equipped with a check valve (A17) and a high-pressure pipeline filter (A5). 17) The oil pipes of the high-pressure pipeline filter (A5) are connected to the parallel oil outlet pipes P1 and P2. The unloading pipe two (A8), which is connected to the oil outlet pipes P1 and P2, is connected to the hydraulic oil tank (A4). The unloading pipe one (A6) and the unloading pipe two (A8) are both equipped with a shut-off valve (A9) and an unloading valve (A10). The unloading pipe two (A8) is equipped with a return oil filter (A11). The hydraulic return oil integrated block (A7) is connected to the return oil pipes T1, R0 and R2. The return oil pipe R1 is connected to the hydraulic oil tank (A4). The drain pipes Y and L are connected to the hydraulic oil tank (A4) through the integrated oil circuit block (A16).

3. The hydraulic system for coordinated operation of multiple working devices in a rail engineering vehicle according to claim 2, characterized in that: The hydraulic power pump assembly (A) also includes an electric emergency pump (A12) and a hand-cranked manual pump (A13). The oil suction ports of the electric emergency pump (A12) and the hand-cranked manual pump (A13) are connected to the hydraulic oil tank (A4) through the oil suction filter (A3). The oil outlet of the electric emergency pump (A12) is connected to the oil inlet of the Y-type oil pipe (A14) equipped with a one-way valve (A17). One oil outlet port of the Y-type oil pipe (A14) is connected to the oil outlet pipe P0 in one direction. The other oil outlet of the Y-type oil pipe (A14) is connected to the oil outlet pipe P2 and the unloading pipe two (A8). An overflow valve one (A15) is installed on the other oil outlet of the Y-type oil pipe (A14).

4. The hydraulic system for coordinated operation of multiple working devices in a rail engineering vehicle according to claim 1, characterized in that: Multiple load-sensitive reversing lines (B1) are connected in parallel to the high-pressure line of the follow-up pressure control module (B2), and the multiple load-sensitive reversing lines (B1) are respectively connected to each hydraulic actuator in the first hydraulic actuation part. The oil inlet of the follow-up pressure control module (B2) is connected to the oil outlet P0 in the hydraulic power pump group (A), and the control oil required in the multiple load-sensitive reversing lines (B1) is taken from the oil outlet P0.

5. The hydraulic system for coordinated operation of multiple working devices in a rail engineering vehicle according to claim 4, characterized in that: The two ends of the oil pipe equipped with the relief valve 2 (B2-3) are connected to the upstream oil outlet pipe P0 and the oil return pipe R0, respectively. The two ends of the oil pipe located downstream of the relief valve 2 (B2-3) and equipped with the pressure compensation valve 1 (B2-1) are connected to the oil outlet pipe P0 and the oil return pipe R0, respectively. The sensitive hydraulic oil pipe (B2-4) located downstream of the pressure compensation valve 1 (B2-1) and equipped with the pilot control valve (B2-2) is connected to the oil outlet pipe P0, and the pressure relief line of the pilot control valve (B2-2) is connected to the drain pipe Y. Multiple load-sensitive reversing lines (B1) are connected in parallel on the sensitive hydraulic oil pipe (B2-4) downstream of the pilot control valve (B2-2).

6. The hydraulic system for coordinated operation of multiple working devices in a rail engineering vehicle according to claim 5, characterized in that: One end of the oil pipe equipped with the first electro-proportional pressure reducing valve (B1-1) and the oil pipe equipped with the second electro-proportional pressure reducing valve (B1-2) are connected in parallel to the sensitive hydraulic oil pipe (B2-4), while the other end is connected to the corresponding interface of the first directional valve (B1-4); the upstream end of the oil pipe equipped with the second pressure compensation valve (B1-3) is connected to the load pressure pipe LS through the shuttle valve (B1-5), the control oil of the second pressure compensation valve (B1-3) is taken from the outlet oil pipe P0, and the downstream end of the second pressure compensation valve (B1-3) is connected to the first directional valve (B1-4), and the two interfaces of the first directional valve (B1-4) are connected to the rodless chamber and the rod chamber of the corresponding hydraulic actuator in the first hydraulic actuation part through oil pipes respectively; The oil pipes connected to the two ports of the first reversing valve (B1-4) and the control oil in the first reversing valve (B1-4) are respectively connected to the return oil pipe R0 through the third overflow valve (B1-6); the first reversing valve (B1-4) is a three-position seven-way reversing valve.

7. The hydraulic system for coordinated operation of multiple working devices in a rail engineering vehicle according to claim 6, characterized in that: The first hydraulic actuator includes multiple hydraulic cylinders in the scissor lift mechanism (1), multiple hydraulic cylinders in the rotary platform lift mechanism (20), multiple hydraulic cylinders in the rotary platform leveling mechanism (18), a hydraulic motor in the rotary platform slewing mechanism (17), multiple hydraulic cylinders in the rotary platform telescopic mechanism (12), and a hydraulic cylinder in the auxiliary platform lift mechanism (15). The rodless chamber and rod chamber of the hydraulic cylinder in (15) are respectively connected to the oil supply pipe in the corresponding load-sensitive reversing pipeline (B1), and the two oil ports of the hydraulic motor in the rotating platform slewing mechanism (17) are respectively connected to the two oil pipes in the corresponding load-sensitive reversing pipeline (B1); wherein, the multiple hydraulic cylinders in the scissor platform lifting mechanism (1), the multiple hydraulic cylinders in the rotating platform lifting mechanism (20) and the hydraulic cylinders in the auxiliary platform lifting mechanism (15) are all connected to the return oil pipe T1 through the oil pipe with the emergency drain valve (B3), and the hydraulic motor in the rotating platform slewing mechanism (17) is connected to the drain oil pipe L through the oil pipe.

8. The hydraulic system for coordinated operation of multiple working devices in a rail engineering vehicle according to claim 1, characterized in that: The high-pressure oil port of the hydraulic metering circuit one (C1) is connected to the oil outlet pipe P1, and the oil return port of the hydraulic metering circuit one (C1) is connected to the oil return pipe R1; the high-pressure oil port of the hydraulic metering circuit two (C2) is connected to the oil outlet pipe P2, and the oil return port of the hydraulic metering circuit two (C2) is connected to the oil return pipe R2.

9. The hydraulic system for coordinated operation of multiple working devices in a rail engineering vehicle according to claim 8, characterized in that: The upstream end of the working oil pipe (C1-5) is connected to the outlet oil pipe P1. The inlets of the multiple reversing oil inlet connectors 1 (C1-3) and 2 (C1-4) are connected in parallel to the working oil pipe (C1-5). The main relief valve (C1-2), which is used to limit the highest working pressure on the hydraulic quantitative circuit 1 (C1) control circuit, is connected to the outlet oil pipe P1 and the return oil pipe R1. The return oil ports of the multiple reversing oil inlet connectors 1 (C1-3) and 2 (C1-4) are connected to the return oil pipe R1. The reversing oil inlet connector (C1-3) includes a three-position four-way solenoid reversing valve (C1-31). The oil inlet and return port of the three-position four-way solenoid reversing valve (C1-31) are connected to the oil outlet pipe P1 and the oil return pipe R1, respectively. The two working oil ports of the three-position four-way solenoid reversing valve (C1-31) are connected to the rodless chamber and rod chamber of the corresponding hydraulic actuator in the second hydraulic actuator section through the oil supply pipes of two parallel overflow valves (C1-32) with opposite flow directions. The reversing oil inlet connector 2 (C1-4) includes a three-position four-way solenoid reversing valve 2 (C1-41) and a one-way throttle valve (C1-42). The oil inlet and return port of the three-position four-way solenoid reversing valve 2 (C1-41) are connected to the oil outlet pipe P1 and the oil return pipe R1, respectively. The two working oil ports of the three-position four-way solenoid reversing valve 2 (C1-41) are connected to the rodless chamber and the rod chamber of the corresponding hydraulic actuator in the second hydraulic actuator part through two oil supply pipes that install the one-way throttle valve (C1-42). The hydraulic quantitative circuit two (C2) includes a multi-way reversing oil inlet three (C2-1) and a working pressure switching valve group (C2-2). The oil inlets of the multi-way reversing oil inlet three (C2-1) are connected in parallel to the oil outlet pipe P2, and the oil return ports of the multi-way reversing oil inlet three (C2-1) are connected in parallel to the oil return pipe R2. The working pressure switching valve group (C2-2) includes a solenoid reversing valve (C2-21) and two overflow valves five (C2-22) connected in parallel to the two working oil port pipes of the solenoid reversing valve (C2-21). The oil inlet of the solenoid reversing valve (C2-21) is connected to the upstream section of the oil outlet pipe P2, and the oil return port of the solenoid reversing valve (C2-21) is connected to the downstream section of the oil return pipe R2. The reversing oil inlet joint three (C2-1) and the multi-way reversing oil inlet joint two (C1-4) have the same structure.

10. The hydraulic system for coordinated operation of multiple working devices in a rail engineering vehicle according to claim 9, characterized in that: The second hydraulic actuator includes multiple hydraulic cylinders in the vehicle primary locking (22), multiple hydraulic cylinders in the vehicle secondary locking (21), multiple hydraulic cylinders in the auxiliary platform guardrail lifting mechanism (13), multiple hydraulic cylinders in the telescopic platform guardrail lifting mechanism (11), multiple hydraulic cylinders in the rotating platform guardrail lifting mechanism (7), multiple hydraulic cylinders in the scissor lift guardrail lifting mechanism (2), multiple hydraulic cylinders in the scissor platform guardrail locking mechanism (3), multiple hydraulic cylinders in the scissor platform locking mechanism (4), multiple hydraulic cylinders in the scissor platform ramp retraction mechanism (5), and multiple hydraulic cylinders in the rotating platform ramp retraction mechanism (6). Hydraulic cylinders, multiple hydraulic cylinders in the rotating platform guardrail locking mechanism (8), multiple hydraulic cylinders in the telescopic platform guardrail locking mechanism (10), multiple hydraulic cylinders in the auxiliary platform guardrail locking mechanism (14), multiple hydraulic cylinders in the rotating telescopic platform locking mechanism (9), hydraulic cylinders in the rotating platform leveling locking mechanism (19), and hydraulic cylinders in the auxiliary platform locking mechanism (16); wherein, multiple hydraulic cylinders in the vehicle primary system locking (22) are connected in parallel to the oil supply pipe of one of the reversing oil inlet lines (C1-3), and multiple hydraulic cylinders in the vehicle secondary system locking (21) are connected in parallel to another reversing oil inlet line (C1-3). The oil supply pipes of the auxiliary platform guardrail lifting mechanism (13), telescopic platform guardrail lifting mechanism (11), rotating platform guardrail lifting mechanism (7), scissor lift guardrail lifting mechanism (2), scissor platform guardrail locking mechanism (3), scissor platform locking mechanism (4) and scissor platform ramp retraction mechanism (5) are connected in parallel to the corresponding reversing oil inlet connection two (C1-4) oil supply pipes; the multi-way reversing oil inlet connection two (C1-4) is connected in parallel to the multiple hydraulic cylinders of the auxiliary platform guardrail lifting mechanism (13), telescopic platform guardrail lifting mechanism (11), rotating platform guardrail lifting mechanism (7) and scissor lift guardrail lifting mechanism (2). The two oil supply pipes of the joint are connected through an oil pipe equipped with a one-way balance valve (C1-43) and used to limit the descent speed of the oil cylinder, and one of the oil supply pipes is connected to the return oil pipe T1 through an emergency oil pipe equipped with an emergency oil drain stop valve (C1-44); the oil supply pipes of the multi-way reversing oil inlet joint three (C2-1) are respectively connected to the hydraulic cylinders in the rotating platform plate retraction mechanism (6), rotating platform guardrail locking mechanism (8), telescopic platform guardrail locking mechanism (10), auxiliary platform guardrail locking mechanism (14), rotating telescopic platform locking mechanism (9), rotating platform leveling locking mechanism (19), and auxiliary platform locking mechanism (16).

Images